EP2657794B1 - Federwelle und Zugfeder - Google Patents

Federwelle und Zugfeder Download PDF

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Publication number
EP2657794B1
EP2657794B1 EP12165537.7A EP12165537A EP2657794B1 EP 2657794 B1 EP2657794 B1 EP 2657794B1 EP 12165537 A EP12165537 A EP 12165537A EP 2657794 B1 EP2657794 B1 EP 2657794B1
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EP
European Patent Office
Prior art keywords
spring
barrel
arbor
profile
axis
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Application number
EP12165537.7A
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English (en)
French (fr)
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EP2657794A1 (de
Inventor
Laurent Kaelin
Arthur Queval
Marco Rochat
Thierry Conus
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
ETA SA Manufacture Horlogere Suisse
Original Assignee
ETA SA Manufacture Horlogere Suisse
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Publication date
Application filed by ETA SA Manufacture Horlogere Suisse filed Critical ETA SA Manufacture Horlogere Suisse
Priority to EP12165537.7A priority Critical patent/EP2657794B1/de
Priority to EP13163792.8A priority patent/EP2674817B1/de
Priority to US13/869,480 priority patent/US9317013B2/en
Priority to RU2013119128A priority patent/RU2609397C2/ru
Priority to CN201310148320.7A priority patent/CN103376727B/zh
Priority to JP2013092016A priority patent/JP5749760B2/ja
Publication of EP2657794A1 publication Critical patent/EP2657794A1/de
Priority to HK14103820.4A priority patent/HK1190805A1/zh
Application granted granted Critical
Publication of EP2657794B1 publication Critical patent/EP2657794B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B1/00—Driving mechanisms
    • G04B1/10—Driving mechanisms with mainspring
    • G04B1/16—Barrels; Arbors; Barrel axles
    • G—PHYSICS
    • G04—HOROLOGY
    • G04B—MECHANICALLY-DRIVEN CLOCKS OR WATCHES; MECHANICAL PARTS OF CLOCKS OR WATCHES IN GENERAL; TIME PIECES USING THE POSITION OF THE SUN, MOON OR STARS
    • G04B1/00—Driving mechanisms
    • G04B1/10—Driving mechanisms with mainspring
    • G04B1/18—Constructions for connecting the ends of the mainsprings with the barrel or the arbor
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/49579—Watch or clock making
    • Y10T29/49581—Watch or clock making having arbor, pinion, or balance

Definitions

  • the invention relates to a method for manufacturing a watch drum shaft.
  • the invention also relates to a method for producing a clockwork motor element, comprising at least one mainspring and a barrel shaft, in which said coil spring of a certain type with first internal turn with a defined width and thickness and said first inner turn comprising, for its maintenance on a barrel shaft, at an inner end, defined profile hooking means
  • the invention also relates to a method for producing a clockwork mechanism comprising at least one motor element produced by such a method of producing a clockwork motor element.
  • the invention relates to the field of watchmaking, and more particularly the field of motor mechanisms.
  • the increase in the capacity of the clockwork motor mechanisms is limited by the volume available at the barrels comprising the energy storage springs. This available volume is delimited by the space available in the movement, therefore by the size of the drum incorporating the spring, and by the geometry of the barrel shaft which must be sized to safely transmit the maximum torque.
  • the invention proposes to improve the capacity of watch cylinders by the use of barrel shafts of the smallest possible diameters, in order to favor the volume allocated to the spring, or the springs if there are any. several, and therefore increase the power reserve of such barrels.
  • the morphology of the shaft conditions the attachment of the spring on the shaft, whose reliability must be ensured to avoid unnecessary dismantling. All things being equal, especially with regard to the materials and heat treatments used for the production of shafts and springs, it is the shape of the shaft, the shape of the spring, but also the type of connection between the spring and the tree, which condition a perfect behavior of the motor element that they compose together.
  • the reduction, in a significant factor, of the shaft diameter compared to conventional fabrications, imposes, still, a decrease in the radius of curvature of the first internal turn of the spring, and those following it.
  • the combined design of the shaft, of the associated spring, and of their mode of attachment or training must take this constraint into account, to prevent any triangulation or facetisation of the spring at its innermost level, which would reduce its duration. life.
  • the invention relates to a method for manufacturing a watch-barrel shaft, in which in a first drawing operation a bar is drawn so as to make it protruding with respect to a profile bearing sector.
  • a bar is drawn so as to make it protruding with respect to a profile bearing sector.
  • circular or helically around an axis parallel to or coincident with that of said bar at least one continuous profile whose section corresponds to the projection, in a plane perpendicular to said axis, complementary attachment means to achieve on said shaft, and in that, in a second machining operation about an axis parallel to or coincident with said axis of the bearing sector, at the level of said continuous profile, upper and lower delimiting faces of a hook are rotated to cooperate with a spring eyelet, and upper and lower lands are rotated for pivotal guidance of said shaft.
  • said continuous profile is that of a hook conjugated to a housing and having a profile corresponding to that of an eyelet which has an inner end of the first inner turn of a spiral band spring barrel of a certain type.
  • the invention also relates to a method for producing a clockwork motor element, comprising at least one mainspring and a barrel shaft, in which said coil spring of a certain type with first internal turn with a defined width and thickness and said first inner turn comprising, for its maintenance on a barrel shaft, at an inner end, defined profile hooking means, characterized in that one carries out said barrel shaft by such a method of manufacturing a watch-dog shaft, said shaft comprising means for pivoting guidance about a pivot axis, and comprising at least one bearing sector for the support a said first internal turn of at least one said barrel spring, said shaft having complementary coupling means complementary profile to said profile of said attachment means for its operation in pivoting with said at least one spring.
  • said shaft comprises, internally recessed with respect to a cylinder, or with respect to a prism of helical section and parallel to the axis of pivoting of said shaft, comprising said bearing sector, at at least one cavity for receiving said hooking means and / or at least a portion of said first internal turn, and said at least one cavity has a plurality of tangential grooves parallel to said pivot axis and each of profile corresponding to that a boss that includes the first inner turn of a spiral band spring barrel of a specific type, said grooves being angularly equidistant around a cylinder, or around a helical section prism and parallel to the pivot axis of said shaft, including said bearing sector.
  • said spring comprises a series of bosses in a number less than or equal to that of said grooves, spaced apart from the same curvilinear pitch as said grooves, and arranged to fit into said grooves.
  • said defined thickness of said first internal turn of the spring is less than the thickness of the following turns of the spring. which are of constant or progressive section away from said first inner turn.
  • At least said inner end of said first inner coil of the spring comprises, on its inner face intended to bear on said bearing sector of said shaft, a roughness greater than 12 micrometers Ra.
  • At least one said spring is welded to said shaft at two points substantially diametrically opposed with respect to said axis of the bearing sector.
  • At least one said spring is held without play in an annular groove of said shaft around said bearing sector or in a straight groove of the shaft along a generatrix of said shaft, and said inner end or at least a portion of said first turn is irreversibly maintained in said groove by welding or brazing or hammering at deformation zones.
  • the invention also relates to a method for producing a clockwork mechanism comprising at least one motor element produced by such a method for producing a clockwork motor element, characterized in that said mechanism is a cylinder, or a movement incorporating at least one barrel, or a timepiece incorporating at least one movement incorporating at least one barrel.
  • the invention relates to a method for manufacturing a watch drum shaft 1.
  • a bar 50 in a first drawing operation, is drawn so as to project, projecting or retracting with respect to a bearing sector 2 with a circular profile or in a helix around a parallel DC axis or coinciding with that of the bar 50, at least one continuous profile 30.
  • the section of this continuous profile 30 corresponds to the projection, in a plane perpendicular to the DC axis, of additional coupling means 3 to be produced on the shaft 1, in profile complementary to the attachment means 13 of a spring 10 of a given type, for the attachment of which the corresponding shaft 1 is designed.
  • the drawing by wire drawing gives the surface surfaces a better fatigue resistance, and ensures a better distribution of the stresses on salient or re-entrant reliefs, in comparison with machining technologies with small radius tools, which create high stress concentrations. , especially in the re-entrant angles, which weaken the tree.
  • the hardening resulting from the drawing process concerns the entire peripheral surface, and in particular the gripping zones, which thus retain a high surface hardness and good wear resistance.
  • this prism in the sense of the descriptive geometry, a solid built along generatrices parallel to the same axis, in elevation on the basis of a closed plane profile.
  • this prism is a right prism, whose generatrices are parallel to a DC axis, and perpendicular to a particular profile, in particular circular, or in a helix.
  • This profile when it is chosen in a helix, is then constructed as a function of the thickness of the first internal turn 11 of a spring 10 with which the shaft 1 is intended to cooperate, and the increase of the helix on its periphery is close to the thickness EI of this first turn 11, and calculated so that, when the first turn 11 of this spring is wound on the shaft 1, it carries permanently, or at least as much as possible , on the support sector 2 constituted by the lateral surface of this prism with helical section.
  • the spring 10 comes into recovery of the inner end 12 that includes the first inner turn 11, it is not deformed by a bearing discontinuity between the bearing surface 2 and the end 12.
  • the Figures 1A, 1B , and 1M illustrate different section profiles after drawing, non-limiting, and well suited to the manufacture of barrel shafts.
  • the continuous profile 30 is straight, that is to say defined by generatrices parallel to the axis of the bar 50. A twisted execution is possible, but generates a higher cost, and the present description is limited to the presentation of continuous 30 straight profiles.
  • the manufacture of a shaft 1 is related to the intended use of this shaft 1 with a coil spring 10 in a spiral band of a certain type, or belonging to a family of springs with common features as regards their interface with the barrel shaft.
  • This interface concerns especially the first inner turn 11, which has an inner free end 12.
  • This first turn 11 has a defined width LI and a defined thickness EI. This does not prevent the realization of the inner end 12 with another profile, and / or another width, and / or another thickness, as will be seen in the following description.
  • the inner free end 12 has or not an eyelet 16, for example stamped, or resulting from the folding of a leg stamped three-quarters, as visible on the Figures 7A and 7B .
  • the free end 12 may also include a cutout of particular shape, as will be explained below, and as visible for example on the Figures 9C , 17A, 17B .
  • FIG. 1 M illustrates the case of any hooking relief with a continuous profile both projecting and retreating, and its inscription, as well as a surface with cylindrical surfaces 2, in the envelope of the bar 50.
  • the first internal turn 11 of the spring 10 is welded by two diametrically opposite points, and preferably at the level of flats 36 or 37.
  • the figure 2 illustrates an advantageous embodiment on the basis of a drawn profile, and which ensures a good maintenance of the spring: this figure 2 illustrates the production of a barrel shaft 1 with hook 34, by a first drawing operation according to the Figure 2A , with a continuous profile 30 according to the Figure 1A or 1B in a variant where the continuous profile 30 is that of a hook 34 conjugated to a housing 35 which allows a better recovery of the first inner turn 11 by the next turn.
  • the profile of the hook 34 conjugated to this housing 35 corresponds to that of an eyelet 16 which has an inner end 12 of the first inner turn 11 of a spiral band spring barrel 10 of a certain type.
  • FIGS. 5C and 5D illustrate an advantageous variant of spring 10 stamped so as to create, between parallel slots according to the elongation of this spring, at least one folded median tab forming a projection protruding from the rest of the surface of the spring 10.
  • This configuration brings the advantage of allowing the recovery of the frolic spring. It is usable, not only in this particular case where it is advantageous to cooperate at least one such boss 15 with grooves 33 of a shaft 1, but also in the general case where it is desired to position precisely, according to the direction of the barrel axis (or else of a balance shaft, or any axis intended to receive a spiral spring clock), such a spiral spring, and in particular, in the case of a barrel, by relative to the drum, and to the possible cover.
  • FIGS 9C and 9D show a particular variant of spring 10, having an end 12 in tee, with a head 18 of length LT connected to the rest of the spring 10 by a core 19, preferably adjacent to the chamfers 19A for better support in winding the spring.
  • the width LG is greater than or equal to, and preferably equal to, this length LT of a transverse bar.
  • the Figure 17A illustrates a particular embodiment of the internal end of the dovetail spring, to cooperate with an antagonistic profile formed on the shaft, here having two shoulders.
  • the Figure 17B illustrates a similar variant with a spring end 12 having two clearances cooperating in stop with two pins stuck in the corresponding shaft1; preferably, the end 12 of the spring 10 is embedded in a circular groove 44, resting on a groove flank 46 of at least one side, and preferably on both sides.
  • the method of manufacturing such a shaft 1 advantageously comprises a machining operation means 7 for driving a ratchet, by threading or tapping or turning or milling facets, as visible on the figure 19 where these drive means 7 are constituted by a conventional square.
  • the Figures 8A and 8B represent a shaft 1 having a front groove 41 opening through an opening 42, and receiving the inner end 12 of the spring 11, made by a method which comprises a machining operation of a front groove 41 of revolution about an axis DG parallel or coincident with the pivot axis D, the front groove 41 being of width LH equal to a defined width LI of the first inner turn 11 of a spiral band spring barrel 10 of a determined type.
  • machining operation further comprises machining at least one opening 42 in an outer wall 43 of the front groove 41, the opening 42 being of greater width than a defined thickness El of the first inner turn 11 of a spring barrel 10 in spiral band of a determined type, for the passage of this first inner turn 11.
  • a surface roughness is imparted to at least a portion of the axis bearing sector 2.
  • DC in the form of a groove made during the first drawing operation, or a knurling performed during the second machining operation.
  • This roughness allows a maintenance by friction between the shaft and the spring, especially if the spring comprises, at the first inner coil 11, on its face facing the axis of the shaft 1, a similar friction surface.
  • a friction surface may, as an alternative to this mechanical development, result from a surface treatment, a metallization type projection, or the like.
  • the invention relates to a driving element 100 of a watch cylinder, comprising at least on the one hand a coil spring 10 of a certain type having a first internal turn 11 with a width L1 and a thickness E1 defined and the first inner turn 11 comprising, for its maintenance on a barrel shaft 1, at an inner end 12, fastening means 13 of profile 14 defined.
  • This motor element 10 further comprises a barrel shaft 1 preferably derived from drawing a bar 50 and made by one of the methods described above.
  • This shaft 1 comprises pivoting guide means 5, 6, around a pivot axis DP, and comprises at least one bearing sector 2 for the support of such a first inner turn 11 of at least one such a mainspring spring 10, the shaft 1 comprising complementary coupling means 3 of profile 314 complementary to the profile 14 of the attachment means 13 for its cooperation in pivoting with this at least one spring 10.
  • the complementary fastening means 13 of the shaft 1 are respectively recessed or in salient relief.
  • the shaft 1 comprises, internally recessed with respect to a cylinder, or with respect to a helical section prism and parallel to the axis of pivoting of the shaft 1, comprising the sector 2, at least one cavity 4 for receiving the attachment means 13 and / or at least a part of the first inner turn 11.
  • this cavity 4 comprises a front groove 41 whose width LH is arranged for the clearance clearance of the spring 10.
  • the front groove 41 is of revolution about a parallel axis DG or coincides with the axis of pivoting D, and its width LH is equal to the defined width LI of the first inner turn 11 of a said mainspring spring 10.
  • the shaft 1 has at least one opening 42 in an outer wall 43 of the front groove 41, this opening 42 being wider than the defined thickness EI of the first inner turn 11, for the passage of the first inner turn 11.
  • this opening 12 is wide enough to allow the maintenance of the first turn 11 without excessive stress, while being small enough to ensure a good maintenance of the end 12 of the spring 10.
  • the central angle in which this opening is between 120 ° and 180 °.
  • the shaft 1 comprises, internally recessed with respect to a cylinder, or with respect to a helical section prism and parallel to the axis of pivoting of the shaft 1, comprising the support sector 2, at least one cavity 4 for receiving the attachment means 13 and / or at least a portion of the first inner turn 11.
  • the axis DC of the bearing sector 2 is parallel or coincident with the axis Pivot D, and at least one such cavity 4 is dimensioned for receiving without play, in the direction of the width LI of the spring 10, the inner end 12 or at least a portion of the first inner coil 11.
  • Figure 11B illustrates a shaft 1 having substantially parallel to each other; a plate 47 and a slot 48 housing the inner coil 11 of the spring 10: its inner end 12 is supported on the plate 47, and the coil 11 is slid into the slot 48.
  • the defined thickness EI of the first inner turn 11 of the spring 10 is less than the thickness ES of the following turns of the spring 10, which subsequent turns are of constant section between them, or of progressive section in s' away from the first inner turn 11.
  • This embodiment is applicable to all the variants of barrel shafts described here, and it allows an optimal plating of the first inner turn 11 on the shaft 1, and in particular on the cylindrical sector (s) which 'it comprises.
  • the free end 12 comprises a chamfer 121 or a radius, so as to allow a good winding of the next turn.
  • At least the inner end 12 of the first inner turn 11 of the spring 10 comprises, on its inner face intended to bear on the bearing sector 2 of the shaft 1, a roughness greater than 12 micrometers Ra.
  • the relative retention between the spring 10 and the shaft 1 can be provided by removable and complementary means, such as eyelet and hook, or the like. In an alternative, it can be ensured by a permanent connection between them, by a method of fixing, in particular irreversible, by welding, brazing, bonding, or the like.
  • at least one such spring 10 is welded to the shaft 1 at two points 51, 52 that are substantially diametrically opposed with respect to the axis DC of the bearing sector 2.
  • shafts 1 designed specifically for springs 10 of a given type allow the counter elements to be dimensioned so as to ensure a play-free assembly of the one on the other.
  • at least one such spring 10 is held without play in an annular groove 44 of the shaft 1 around the bearing sector 2, or in a straight groove 45 of the shaft 1 along a generatrix of the shaft 1 .
  • the inner end 12, or at least a part of the first turn 11, is irreversibly maintained in such a groove 44, 45, by welding or soldering, or else very economical way, by hammering or local crushing at the level of deformation zones 53, at the level of the spring 10 and / or at the level of the shaft 1.
  • the figure 16C illustrates a spring 10 mounted fitted and projecting in a circular groove 44 of a shaft 1, and hammered in position for its retention, in particular by the action of a wheel or the like, so as to create deformation surfaces 53 immobilizing the spring relative to the shaft.
  • the figure 16D similarly illustrates, and preferred in the usual case where the hardness of the spring is greater than that of the shaft, an application where the wheel is applied to the walls of a groove in which the spring is gripped to imprison it under deformation zones 53.
  • All the above-mentioned configurations are suitable for stopping the spring 10 on the shaft 1 by a welding point, laser welding (radial or parallel to the axis), brazing, bonding, or the like.
  • the invention also relates to a timepiece mechanism 1000 comprising at least one such motor element 100.
  • This mechanism 1000 is a cylinder 200, or a movement 300 incorporating at least one cylinder 200, or a timepiece 400 incorporating at least one movement 300 incorporating at least one cylinder 200.

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  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Springs (AREA)
  • Metal Extraction Processes (AREA)
  • Ropes Or Cables (AREA)
  • Wire Processing (AREA)

Claims (9)

  1. Verfahren zum Herstellen einer Uhrenfederwelle (1), bei dem in einem ersten Ziehvorgang ein Stab gezogen wird, derart, dass mindestens ein durchgehendes Profil (30) ausgebildet wird, das in Bezug auf einen Auflagebereich (2) mit kreisförmigem oder spiralförmigem Profil um eine Achse (DC) parallel oder zusammenfallend mit jener des Stabs vorsteht, wobei der Querschnitt des durchgehenden Profils (30) dem Überstand von komplementären Einhakmitteln (3) in einer Ebene senkrecht zu der Achse (DC) entspricht, die auf der Welle (1) auszubilden sind, und dass in einem zweiten Drehvorgang um eine Achse parallel zu oder zusammenfallend mit der Achse (DC) des Auflagebereichs (2) auf Höhe des durchgehenden Profils (30) eine obere (34A) und eine untere (34B) Begrenzungsfläche eines Hakens (34) gedreht werden, um mit einer Federöse zusammenzuwirken, und eine obere (5) und eine untere (6) Lauffläche für die rotatorische Führung der Welle (1) gedreht werden.
  2. Verfahren für die Herstellung einer Uhrenfederwelle (1) nach Anspruch 1, dadurch gekennzeichnet, dass zumindest einem Teil des Auflagebereichs (2) gemäß der Achse (DC) eine Oberflächenrauheit von mehr als 12 Mikrometer Ra in Form einer Riffelung, die bei dem Ziehvorgang ausgebildet wird, verliehen wird.
  3. Verfahren zur Herstellung einer Uhrenfederwelle (1) nach einem der Ansprüche 1 oder 2, dadurch gekennzeichnet, dass zumindest einem Teil des Auflagebereichs (2) gemäß der Achse (DC) eine Oberflächenrauheit von mehr als 12 Mikrometer Ra in Form einer Rändelung, die bei dem Vorgang der Wiederaufnahme der spanabhebenden Bearbeitung ausgebildet wird, verliehen wird.
  4. Verfahren für die Herstellung eines Uhrenfederhaus-Antriebselements (100), das mindestens eine Federhausfeder (10) und eine Federwelle (1) umfasst, wobei eine Federhausfeder (10) aus einem spiralförmigen Band eines bestimmten Typs ausgebildet wird, das eine erste innere Windung (11) mit einer definierten Breite (LI) und einer definierten Dicke (EI) aufweist, wobei die erste innere Windung (11), um sie an einer Federwelle (1) zu halten, auf Höhe eines inneren Endes (12) Einhakmittel (13) mit definiertem Profil (14) aufweist, dadurch gekennzeichnet, dass die Federwelle (1) durch ein Verfahren nach einem der vorhergehenden Ansprüche ausgebildet wird, wobei die Welle (1) Mittel (5, 6) zum rotatorischen Führen um eine Drehachse (DP) umfasst und mindestens einen Auflagebereich (2) aufweist, um eine erste innere Windung (11) mindestens einer Federhausfeder (10) abzustützen, wobei die Welle (1) komplementäre Einhakmittel (3) mit einem Profil (314), das zu dem Profil (14) der Einhakmittel (13) komplementär ist, aufweist, um mit der mindestens einen Feder (10) rotatorisch zusammenzuwirken.
  5. Verfahren für die Herstellung eines Antriebselements (100) eines Uhrenfederhauses nach Anspruch 4, dadurch gekennzeichnet, dass die Federhausfeder (10) aus einem spiralförmigen Band eines bestimmten Typs ausgebildet wird, der an einem inneren Ende (12) der ersten inneren Windung (11) der Feder (10) eine Öse (16) aufweist, und dass das durchgehende Profil (30) durch Ziehen als das Profil eines Hakens (34) ausgebildet wird, der einem Aufnahmeraum (35) zugeordnet ist und ein Profil hat, das jenem der Öse (16) entspricht.
  6. Verfahren für die Herstellung eines Antriebselements (100) eines Uhrenfederhauses nach Anspruch 4 oder 5, dadurch gekennzeichnet, dass die Feder (10) mit einer definierten Dicke (EI) der ersten inneren Windung (11), die kleiner als die Dicke (ES) der folgenden Windungen der Feder (10) ist, die einen konstanten oder mit zunehmender Entfernung von der ersten inneren Windung (11) allmählich zunehmenden Querschnitt besitzen, ausgebildet wird.
  7. Verfahren für die Herstellung eines Antriebselements (100) für ein Uhrenfederhaus nach einem der Ansprüche 4 bis 6, dadurch gekennzeichnet, dass die Feder (10) zumindest mit dem inneren Ende (12) der ersten inneren Windung (11) der Feder (10) ausgebildet wird, die auf der inneren Fläche, die dazu bestimmt ist, sich auf dem Auflagebereich (2) der Welle (1) abzustützen, eine Rauheit größer als 12 Mikrometer Ra besitzt.
  8. Verfahren für die Herstellung eines Antriebselements (100) für ein Uhrenfederhaus nach einem der Ansprüche 4 bis 7, dadurch gekennzeichnet, dass wenigstens eine Feder (10) auf Höhe von zwei Punkten (51, 52), die sich in Bezug auf die Achse (DC) des Auflagebereichs (2) im Wesentlichen diametral gegenüberliegen, an die Welle (1) geschweißt wird.
  9. Verfahren für die Herstellung eines Uhrenmechanismus (1000), der mindestens ein Antriebselement (100) umfasst, das gemäß einem Verfahren nach einem der Ansprüche 4 bis 8 ausgebildet ist, dadurch gekennzeichnet, dass der Mechanismus (1000) ein Federhaus (200) oder ein Werk (300), das wenigstens ein Federhaus (200) enthält, oder ein Zeitmessgerät (400), das wenigstens ein Werk (300) enthält, das wenigstens ein Federhaus (200) enthält, ist.
EP12165537.7A 2012-04-25 2012-04-25 Federwelle und Zugfeder Active EP2657794B1 (de)

Priority Applications (7)

Application Number Priority Date Filing Date Title
EP12165537.7A EP2657794B1 (de) 2012-04-25 2012-04-25 Federwelle und Zugfeder
EP13163792.8A EP2674817B1 (de) 2012-04-25 2013-04-15 Verfahren zur Herstellung eines Uhrfederhauswelle
RU2013119128A RU2609397C2 (ru) 2012-04-25 2013-04-24 Вал барабана и ходовая пружина
US13/869,480 US9317013B2 (en) 2012-04-25 2013-04-24 Method of producing drive element for a timepiece barrel including a barrel arbor and mainspring
CN201310148320.7A CN103376727B (zh) 2012-04-25 2013-04-25 条轴和主发条
JP2013092016A JP5749760B2 (ja) 2012-04-25 2013-04-25 香箱真及びゼンマイ
HK14103820.4A HK1190805A1 (zh) 2012-04-25 2014-04-22 條軸和主發條

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EP12165537.7A EP2657794B1 (de) 2012-04-25 2012-04-25 Federwelle und Zugfeder

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EP2657794A1 EP2657794A1 (de) 2013-10-30
EP2657794B1 true EP2657794B1 (de) 2017-02-01

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EP13163792.8A Active EP2674817B1 (de) 2012-04-25 2013-04-15 Verfahren zur Herstellung eines Uhrfederhauswelle

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EP (2) EP2657794B1 (de)
JP (1) JP5749760B2 (de)
CN (1) CN103376727B (de)
HK (1) HK1190805A1 (de)
RU (1) RU2609397C2 (de)

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JP5749760B2 (ja) 2015-07-15
RU2013119128A (ru) 2014-10-27
CN103376727B (zh) 2016-02-10
RU2609397C2 (ru) 2017-02-01
US9317013B2 (en) 2016-04-19
US20130283615A1 (en) 2013-10-31
JP2013228393A (ja) 2013-11-07
EP2657794A1 (de) 2013-10-30
HK1190805A1 (zh) 2014-07-11
EP2674817A3 (de) 2017-05-17
CN103376727A (zh) 2013-10-30
EP2674817A2 (de) 2013-12-18
EP2674817B1 (de) 2020-05-27

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